Braking system



Sept 7, 1937. c. c. FARMER 2,092,416

BRAKING SYSTEM OLYDE C. FARMER ATTORN EY 5 sneets-shet 2 Umu- Pw. O

I INVENTOR CLYDE O. FARMER ATToRN Sept. 7, 1937. c. c. FARMER BRAKING SYSTEM Filed July 17, 1936 :s sheds-sheet' s I INVENTOR CLYDE C. FARMER l ATTORNEY Patented Sept. 7,1937

amant UNITED STATES PATENT @FFME BRAKING SYSTEM n oiyee o. ramer, Pittsburgh, Pa., assigner to The Westinghouse Air Brake Company, Wilmerding, Pa., a corporation of Pennsylvania Application July 17, 1936, Serial No. 91,036

This invention relates to 13 Claims.

braking `systems for traction vehicles and railway trains, and more particularly to braking systems employing both uid pressure brakes and magnetic track brakes.

Certain types of modern traction and railway vehicles are provided with rubber inserts between the wheel treads and wheel hubs in order to minimize the noise transmitted to the vehicle body,

for the purpose of producing a quieter operating vehicle. Where such rubber the degree of braking which inserts are employed is permissible on the wheel treads for repeated applications must be limited, because if the wheel treads are permitted to become over-heated the rubber inserts may be wholly destroyed or damaged beyond usefulness.

Since the degree of braking` on the wheel treads must be thus limited, otherbrake means must be employed to produce sufficient braking to stop the vehicle with reasonable promptness;

A preferred type of auxil iary brake means is the magnetic track brake. This type of brake employs one or more magnetic track brake devices which arc normally suspended above the track rail in their release or inoperative position, and are caused to engage the rails in their application position, the exciting windings of the brake devices being at the same time energized so that a braking effect is produced on In brake equipments for vehicles which empl-oy both the track rails. the new quiet type fluid pressure operated brakes and magnetic track brakes, the control is preferably so arranged that for repeated normal or service applications the degree to which the wheel brakes is applied is limited or suppressed, while the magnetic track brakes are conditioned to perform a larger than usual share of the braking. In this manner the heating of the wheel treads, due to braking thereon, is kept to a minimum and the life of the rubber inserts is greatly prolonged. Where, failure of the electric power however, there isa source available for energizing the magnetic track brakes it is desirable that the uid pressure brakes be applied to a greatly increased degree, to loss of track braking.

A principal object of the compensate for the present invention is :legree of application in the tric power supply for the m should fail. 4

event that the elecagnetic track brakes (Cl. 30S- 3) A further object of the pres-ent invention is to provide a brake equipment of the above referred to character in which the pressure of fluid supplied ior operating the fluid pressure brakes is normally limited to moderate values, but which 5 is increased instantly to a considerably larger value upon failure of the electric power supply for the magnetic track brakes. l

A still further object of the invention is to provide a braking system of the aforementioned` 1() character in which improved means are provided for responding to a failure of the electric power supply to condition the fluid pressure bra-ke portion of the system for an application to a maximum degree.

Further objects of the invention dealing with arrangements and associations of related parts will be more clearly understood from the following description of two embodiments of the invention, which are taken in connection with the attached drawings, wherein,

Figs. 1A and 1B, when taken together and placed end to` end, illustrate in schematic and diagrammatic form one embodiment of the invention. g5

Fig. 2 shows a modication which may be made to the braking system of Figs. lA and 1B, and thus illustrates another form of the invention.

Referring now to Figs. 1A and 1B, and considering the brake system thus illustrated briefly :io at rst, I have represented the wheel brakes by the single brake cylinder lil (although any number may be used), which may be employed to operate any of the conventional type wheel brakes. A control valve device Il is provided for 35 controlling the supply of fluid Linder pressure to` i the brake cylinder il). A high pressure magnet valve device l2 and a compensating valve device i3 cooperate-to make available high iluid pressures upon failure of the electric power supply. fio

The main source of supply of fluid under pres-ifi"l sure is' from a main lreservoir iii, which is con- `nected to a suitable compressor (not shown), but the supply for normal .brake applications is regulated by a feed valve device i5 of conventional 45 design. f Y

A brake valve device I5 is provided for manually controlling applications of the brakes, while a deadman control is embodied in the motor controller, diagrammatically shown at il, which cooperates with an application valve device I8. fi.

The magnetic track brake apparatus comprises at least one track brake device I9, which may be `of conventional design, a raising cylinder 2li therefor, and a magnet valve device 2l for con- 55 trolling the supply of fluid under pressure to and its release from the raising cylinder. A fluid pressure operated rheostat device 22 is employed to control the degree of energization of the track brake device I9.

In order to deenergize the track brake device at about the time the vehicle or train comes to a stop, and thus minimize the danger of overheating of the track brake device, there is provided a cut-out relay 23, the energization of which is controlled by the vehicle motors diagrammatically indicated at 24.

Considering now more in detail the devices above enumerated, the control Valve device i comprises a relay portion 26 and an emergency valve portion 21.

The relay valve portion 26 is embodied in a casing provided With a piston 28 which is subject on one side to pressure of uid in a chamber 29 and on its other side to pressure of fluid in a chamber 39. Attached to the piston is a stem 3| provided with shoulders or collars 32 for operating a slide valve 33 with a lost motion movement. For guiding the movement of the piston and slide valve there is provided a guiding element 34 slidable in a coacting bore, and provided with a small port 35 for providing communication between the chamber 39 and slide valve chamber 36.

Upon inward (downward) movement of the piston 28 the slide valve 33 will be actuated to blank exhaust ports 31, and after these portsv are blanked the end of stem 3| will engage the stem 38 of the Valve 39 and unseat the valve against the bias of its spring 40. This establishes a communication between a supply chamber 4| (which is connected to main supply pipe 42) and the slide valve chamber 36, which by way of passage 43 is connected to brake cylinder pipe 44. Fluid under pressure will then ow from the supply pipe 42 and chamber 4| to the brake cylinder I0. Fluid under pressure in chamber 36 will flow also through port 35 to chamber 30, and when the pressure in chamber 39 equals or slightly 45 overbalances the pressure in chamber 29 piston 28 will move outwardly until the valve 39 is seated by spring 40. The supply to the brake cylinder l0 will be then lapped.

If the pressure in chamber 29 is subsequently reduced, then piston 28 will move outwardly (upwardly) far enough for slide valve 33 to uncover the one exhaust port 31 and for port 45 in the slide valve to register with the other exhaust port 31. Fluid under pressure will then be released from the brake cylinder I0. It will, of course, be obvious that if the pressure in chamber 29 is varied in any other manner the brake cylinder pressure will correspondingly vary.

While the relay valve portion 26 has been shown in a vertical position, it is preferably disposed horizontally when installed on a vehicle.

The emergency valve portion 21 is embodied in a casing having a piston 41 subject on one side to the combined pressure of fluid in a charnber 48 and that of a biasing spring 49, and subject on its other side to pressure of luid in a slide valve chamber 50. Attached to the piston 41 is a stem 5| having collars 52 thereon adapted to actua'te a slide valve 53 coextensive with movement of the piston 41. In the release position of the piston 41, as illustrated, a cavity 54 in the slide valve 53 connects two passages 55 and 56.

The chamber 48 is connected by passage 51 to an emergency pipe 58 which, in the release position of piston 41, is charged by Way of feed groove 59 around the piston. The slide valve chamber 50 is connected by a passage 6D to the aforementioned chamber 4|, which is open to the supply pipe 42.

Upon a sudden decrease of pressure in the piston chamber 48, piston 41 moves to its extreme outward position (to the right), carrying with it the slide valve 53. The slide valve then disconnects passage 55 from passage 56, and a port 62 in the slide valve registers with the passage 55, so that fluid under pressure may ow from chamber 59 into this passage. It will be noted that the passage 55 leads to the relay piston chamber 29, while the passage 55 leads by way of pipe 63 to a double check valve device 64. Upon restoring the pressure in the piston chamber 48, the piston 41 and slide valve 53 will return to the illustrated positions, thus reconnecting the double check valve device 64 with the relay piston chamber 29.

The double check valve device 64 is embodied in a casing having disposed therein a slide valve 65 which operates to selectively connect to the pipe 63 either a straight air pipe 66 or a high pressure pipe 61, depending upon in which of the two pipes 66 and 61 the pressure of the iiuid supply is the greater. e

The high pressure magnet valve device I2 is embodied in a casing provided with a release valve 1i) and a supply valve 1| arranged in abutting relationship. A spring 12 urges the supply valve 1| toward unseated position and the release valve 13 toward seated position. An electromagnet 13 in the upper part of the valve device casing functions when energized to hold the release valve 16 unseated and the supply valve 1| seated.

The compensating valve device I3 is embodied in a casing having suitably disposed therein two flexible diaphragms 14 and 15 so arranged as to dene therebetween a pressuretight chamber 16. The two diaphragms are provided with the usual follower plates and are rigidly interconnected by a stem 11, so that as one diaphragm moves the other moves also. A spring 84 acting on the one side of the diaphragm 14 biases the two diaphragms to a position such that diaphragm 15 seats on a seat rib 18. This closes a communication between the aforementioned high pressure pipe 61 leading to the double check valve device 64 and another pipe 19 leading to the high pressure magnet valve device I2.

The spring 84 is strong enough to maintain the diaphragm 15 seated on seat rib 18 for the highest pressure of fluid which may be established below the diaphragm 15 within the seat rib 18.

The chamber 16 is, however, connected to the brake cylinder pipe 44, so that when a predetermined brake cylinder pressure is obtained the differential of pressure acting on the diaphragm 14, together with the pressure acting below the diaphragm 15 within the seat rib 18, will unseat the diaphragm 15 and thus establish communication from the pipe 19 to the pipe 61.

It will be noted that a one-way check valve device 86 provides a one-way communication from the pipe 61 to the pipe 19. The purpose of this will be clear later.

The main supply pipe 42 may be selectively in communication with the feed valve device I5 or the aforementioned pipe 19 by way of a second double check valve device 8|. Like the aforedescribed check valve device 64, this check valve is embodied in a casing having a slide valve 82 therein which is actuated to the left or the right depending upon whether the pressure of fluid delivered by the feed valve device I5 or that delivered by the pipe 'I9 is the greater. As will be noted, the feed valve device I5 is connected by a pipe 83 directly to the main reservoir Iii, while the pipe 5 'I9 may be connected to the main reservoir only when the supply valve 1I of the high pressure magnet valve device I2 is unseated.

Considering now the brake valve device I6, this device is provided with an operating handle 85, which according to conventional practice is movable from a release position different degrees into a service application Zone, and beyond this Zone to an emergency position.

As the handle is moved from release position it rotates a shaft Bti having rigidly disposed thereon a cam 8l. This cam is so designed that as the handle is rotated into the service application zone it progressively shifts a plunger 38 to the left. Carried by the plunger and pivotally connected thereto at 89 are two spaced levers Siti. The lower ends of these two spaced levers carry a roller @I which engages the outer end of a release valve 92. This release valve 92 is disposed interiorly of a movable abutment 93 in the form of a piston,

and is normally urged to an unseated position by a spring 94.

Upon the inward (left) movement of the plunger 38 the spaced levers 95 will pivot about their upper ends and rotate in a clockwise direc- 30 tion to seat the release valve @2, thus closing communication between a pressure chamber 95 and the atmosphere, which communication leads by way of passage gli, past the unseated release valve 92, passage 91, spring chamber 98, passage 39 and exhaust pipe Illll. The movable abutment 93 is during this operation held in the illustrated position by a regulating spring IllI.

When the release valve 92 has been seated the spaced levers 90 will fulcrum about their lower 40 ends and rotate in a counterclockwise direction to unseat a supply valve m2 against the bias of its spring |03, which spring is a much stronger spring than the release valve spring 94. Unseatng of the supply valve IM opens a communication between the main supply pipe l2 and the pressure chamber 95, by way of passage Iil. The pressure chamber 95 is connected directly with the straight air pipe 66 so that fluid under pressure flows to this pipe, v

As the pressure builds up in the chamber 95 it acts upon the right side of the movable abutment 93 and progressively compresses the regulating spring IIlI. 'I'his causes the spaced levers 90 to fulcrum about their mid-point and rotate in a clockwise direction under the action of the supply valve spring |03 until the supply valve Iil is seated. The parts are so designed that the pressure at which the sup-ply valve H32 seats corresponds substantially to the degree or extent of movement of the handle 85 into the service application zone. It will thus be obvious that the pressure established and maintained in the pressure chamber 95, and in the straight air pipe 56, corresponds' to the position of the handle 85 in the service application zone.

When the handle 85 is moved to the emergency position the valve mechanism described will be conditioned to establish the maximum pressure in the pressure chamber 95, and at the same time another cam Ill@ on the shaft 55 engages the stem |01 of an emergency vent valve IIlB to unseat this ,valve against the bias of spring m9. Unseating of this valve establishes a communication between the emergency pipe 58 and the exhaust pipe IDD by way of passage I IIJ, past the unseated vent valve |08 and passage Ill. 'I'he pressure in the emergency pipe will thus be reduced as the venting takes place.

It will be noted that a passage I I2 and a choke H3 provide a charging communication from the main supply pipe 42 to the emergency pipe 58, so that the emergency pipe may be recharged by way of this communication when the venting communication is closed, The choke H3 prevents undue loss of fluid under pressure from the l0 charging source when the emergency pipe is being vented.

The motor controller mechanism I'I is provided with an operating handle II5 which in addition to having several rotative motor controlling po- 15 sitions also has an up position and a down position for controlling the brakes. The controller handle is illustrated in its down position, in which position an extension H6 of the handle, beyond its fulcrum point Ill, lifts a stem IIB to permit 20 a bale IIS to be rotated about its fulcrum point I 20 by a spring I2I, so as to seat a release valve I 22. The seating of this release valve closes a communication between a safety control pipe 23 and an exhaust pipe 52d. At the same time, a supply or charging valve l25, which is subject to the pressure of fluid in the main supply pipe. 42, unseats to permit the safety control pipe l23 to be charged from the main supply pipe.

The motor controller handle IE5 is held in its 30 down position by the operator at all times while the vehicle is running. If, however, through accident or design the operator should release the handle IE5 a spring I2@ acting upon a collar l2'I secured to the stem II8 would move the handle 35 to its upper position, whereupon the stem l I8 would rock the bale I i9 about its iulcrum I2@ to unseat the release valve E22 and seat the charging valve IE5. The safety control pipe I23 would thus be vented to the atmosphere. la

Connected to the safety control pipe is the application valve device I8. This valve device is embodied in a casing having a valve I3@ therein in the form of a piston which is subject on its uppermost side to safety control pipe pressure g5 and also the pressure of a biasing spring ISI. A restricted passage E33 forms a communication between the chamber above the valve and the emergency pipe 58. When the safety control pipe is charged the valve I3@ is held upon a seat n() When the safety control pipe pressure is suddenly reduced, the overbalancing pressure acting on the under side of the valve It, outside the seat rib E32, will actuate the valve upwardly, es- 515 tablishing communication between the emergency pipe 58 and an exhaust port i3d, and also closing the restricted communication E33 between the chamber above the valve and the emergency pipe. When the emergency pipe pressure has (50 been reduced to a low value the spring I 3I will again seat the valve ISE.

Considering now the magnetic track brake apparatus, each of the track brake vdevices i9 is provided with a yoke member I35 secured there- `6`5 to and secured to a stem 33 of a piston itl in its associated raising cylinder 2t. When iiuid under pressure is supplied to chamber I33 below piston I3'i the associated track brake device I9 will be held suspended above track rail I39. When the 70 pressure in the chamber i348 is reduced substantially to atmospheric pressure, the force of gravity will cause the track brake device IQ'to drop to engagement with the track rail |39.

The magnet valve device 2l, which controls Z5 the supply of fluid under pressure to and its release from the raising cylinder 25, is embodied in a easing having a release valve |50 and a supply Valve IM arranged in abutting relationship, as illustrated. A spring |52 urges the supply valve Uli toward unseated position and the release valve Edil toward seated position. When the supply valve hlt is unseated and the release valve Ml] is seated, fluid under pressure is supplied from the main supply pipe 42 to the chamber |38 in the raising cylinder 2B.

In the upper part of the magnet valve device casing is an electromagnet |43, which when energized actuates the supply valve |4| to seated position, to cut ci the supply of fluid under pressure to the raising cylinder 2D, and also actuates the release valve |45 to unseated position, to vent the raising cylinder 2i! to the atmosphere by way of exhaust port |28.

The track brake rheostat device 22 is embodied in a casing having disposed therein a flexible diaphragm Mil subject on its uppermost side to pressure of fluid supplied to a chamber |65 and on its lowermost side to atmospheric pressure in a chamber |46, which is always open to the atmosphere by way of port |51.

Operatively connected to the diaphragm |44 by a stem titi is an arm M9 pivoted at one end on a pin |55. Carried by the other end of the arm and insulated therefrom, and from each other, are two contact members |5| and |52. The contact member |51 is adapted when actuated downwardly to cut out sections of a resistance |53 while the Contact member 52 at the same time engages and maintains contact with a stationary contact member |5111.

The arm |419 is normally bia-sed to the illustrated position by a spring |55. The chamber M5 is connected to the brake cylinder pipe lili, and consequently as the brake cylinder pressure increases the arm |59 is actuated downwardly to a corresponding degree.

The description of the relay 23 and its functioning in connection with the vehicle motors 24, and the operation of the motor controller l1, is best understood from a description of the operation o1" 'this embodiment of my invention, which now follows:

Running condition When a vehicle or train equipped with the embodiment of my invention just described is running, the operator maintains the brake valve handle 55 release position, and at the same time maintains pressure manually applied to the motor controller handle |5 so as to maintain. this handle in its down position.

In order to more clearly describe the operation of my invention reference will be had to specific liuid pressures, but it is to be understood that these are used for illustrative purposes only. Assuming now that the main reservoir i4 has been charged to a pressure of eighty pounds (per square inch.) or greater, and that the feed valve l5 has been set to deliver fluid at nity-five pounds (per square inch) pressure, the main supply pipe [s2 will be charged to feed valve pressure, and the emergency pipe 58 will be charged from the main supply pipe through the brake valve device i6 by way of passage H2 and choke H3, as previously described, and also by way of feed groove 59 in the control valve device ll. At the same time, when the motor controller handle I5 is in its down position, the safety control pipe |23 will be similarly charged past the charging valve |25.

The track brake devices I9 will be held suspended above the track rail |39, as the magnet valve device 2| is at this time deenergized.

The high pressure magnet valve device |2 is at all times connected to trolley |55 by way of conductors |51 and |58, the return connection to the source of power supply being by way of ground conductor |59. The supply valve 1| in the high pressure magnet valve will thus be held seated, While the release Valve 1|! will be held unseated.

The other parts will be in the positions as illustrated.

Normal service application The motor controller |1 has been illustrated in the power on position, in which position the trolley |55 is connected to the Vehicle motors 24 by way of conductors |51 and itil, contact fingers |5| and drum contact |52, and conductor |53, the return connection to the source of power supply being by way of ground conductor |64. In order to make a service application of the brakes the operator first moves the motor controller handle H5 to the power oir position, in which position the drum contact 52 disengages from the contact ngers |621, thereby interrupting the power supply to the vehicle motors and at the same time drum Contact |55 engages contact iingers 956. This partially establishes a circuit from the vehicle motors 2li, which will now operate as generators, to the relay 23, this circuit including conductor i5?, contact fingers |66 and drum contact |65, conductor |55, the relay 23, conductor |59, now open contacts |52 and |55 of the track brake rheostat 22, and conductor |10.

The operator then moves the brake valve handle out of release position into the service application zone to a degree or extent according to the desired degree of application oi the brakes. Fluid under pressure will then be supplied to the straight air pipe 55 dependent upon the degree of movement of the brake valve handle. From the straight air pipe 66 iiuid under pressure will flow to the double check valve device 64, where it will shift the slide valve 55 to the right as illustrated, and then iiow by way of pipe 53, passage 56, cavity 54, passage 55, to the relay valve piston chamber 29. The pressure thus established in chamber 29 will actuate the piston 28 inwardly to close the brake cylinder exhaust communication and to unseat the valve 39, to supply fluid under pressure from the main supply pipe i2 to the brake cylinder. The brake cylinder pressure will be lapped when it corresponds to the straight air pipe pressure, the degree of the wheel brake application thus corresponding to the brake valve handle position.

Fluid under pressure iiowing to the brake cylinder ID also iiows to the track brake rheostat 22, where it acts upon the diaphragm Hill to move the arm |45 downwardly. As the arm |49 moves downwardly Contact E52 engages contact |561 to complete the circuit through the relay 23, thus causing the relay to close its contacts |11. Closing of these contacts establishes a circuit to the track brake device i9, which beginning at the trolley |55` includes conductor |51 and i12, relay contacts |1|, conductor 13, now closed contact |5l, a portion of resistance |53, and conductor Elfi, the return connection to the source of power supply being by way of ground conductor |15.

At the same time, the closing of relay contacts |11 also establishes a circuit by way of conductor |15 to the magnet valve device 2|, its return connection being by way of ground conductor |11.

This magnet valve device then seats its supply valve Ml and unseats its release valve |45. Fluid under pressure will thus be released from the raisingcylinder 2l), and the track brake device I9` 5 will drop to engagement with the rail |39 due to the force of gravity.. l

It will thus; be seen that operation of the brake valve handle 85 into the ser'vice application Zone effects an application of both the fluid pressure ...10 brakes and the magnetic track brakes.

In order that the rubber inserts in the wheels shall not be damaged due to excessive overheating resulting from braking on the wheels, I prefer to arrange the parts so that during a service appli- .,15 cation of the brakes the braking load is shared approximately equally between the wheel brakes and the track brakes. Further and with respect to the uid pressures heretofore mentioned, I have in practicing my invention found it desirable 20 to limit (by properly designing the brake valve I6) the brake cylinder pressure which may be established by movement of the brake valve handle into the service zone to a maximum of forty pounds. By thus limiting the brake cylinder pres- 25 sure the danger of damaging the rubber inserts in the wheels due to repeated service applications of the brakes is greatly minimized.

As the vehicle is decelerating under action of the brakes the magnetic track brakes will be v.30 automatically cut out of action at a low vehicle speed regardless of the brake cylinder pressure obtaining. This is accomplished by the deener- I gization of the relay 23 due to the decreasing voltage output of the vehicle motors 24 with the de- `35 crease in speed. The relay 23 is preferably so designed that when the speed of the vehicle dil minishes to approximately iive or six miles per hour, at which time the voltage output of the motors will be low, it will open its contacts Ill 40 and thereby effect a full release of the track brakes.

When it is desired to release the brakes` following a service application, the brake valve handle 85is returned to the release position, in which 45 position the straight air pipe is vented to the atl mosphere, and correspondingly the pressure inthe brake cylinder lll and chamber |45 of the track brakerheostat is reduced.

When switching the vehicle or train about ter- 50 minal yards it is not desirable or necessary to apply the track brakes. Generally speaking, Sunicient braking can be obtained with the wheel brakes alone, evenwithbrake cylinder pressures of fteen pounds or less. I therefor prefer to ar- 55 rangethe traokbrake Yrheostat (by initially Vtensioning the spring |55) so that for brake cylinder pressures below fifteen pounds the track brake `windings will be deenergized. Thus brake cylinder pressures below fifteen pounds may be em- 50 ployed without applying the magetic track brakes. l

Normal emergency application When it is desired to effect an emergency appli- 65 cation of the brakes, this may be accomplished by moving the brake valve handle 85 to the emergency position, and thereby directly ventingthe emergency pipe 58 past the vent valve lil, or by releasing the moto-r controller handle lili and tion, and thus connect the slide valve lchamber 50 and main supply pipeclZ to the relay valve piston chamber `29. Since the pressure maintained in the main supply pipe 42 is fifty-five pounds, as compared to the maximum of forty pounds delivered by the brake valve device I6 in the service application zone, it follows that the brake cylinder pressure which may be established durmg an emergency application will be approximately fifty-five pounds. l

Concomitantly, the track brake rheostat 22 will be operated. to increase the degree of energization of the track brakes, soi that the total degree of braking is greater than for any service application.

If the emergency application was effected by manipulation of the brake valve handle 35, a release may be effected by returning the brake valve handle to its release position and thus closing the communication between the emergency pipe 58 and the atmosphere, and permitting the emergency pipe to be recharged by way of the choke H3.

If the emergency application was eifected as a result of upward movement of the controller handle H5, the release may be eifected by moving this handle to its down position, thus seating the release valve |22 and permitting the safety control pipe to be recharged from the main supply pipe past the charging valve |25. Valve |353 in the application valve vdevice i3 will thus be held 1n a seated position, so that the emergency pipe ci?? be charged through the brake valve choke As the pressure in the emergency pipe builds up emergency piston 41 will return to the illustrated or release position, whereupon fluid under pressure in the relay valve chamber 23 will be released to the atmosphere through the straight air pipe Gil `and past the release valve 92 in the brake Valve. This will, of course, effect a release of iiuid under pressure from the brake cylinder I0 and from the track brake rheostat 22, thus releasing both the wheel brakes and the magnetic track brakes, if the track brakes have not already been released due to operation of relay 23.

Applications lwith. electric power supply cr* As long as the electric power supply is availablel the high pressure magnet valve device l2 will remain energized. The maximum degree of application of the fluid pressure brakes is therefore limited to the pressure of fluid supplied by the feed valve device l5, namely nity-five pounds.

If the source of electric power supply should fail, or if the trolley |55 should disengage from the trolley wire, the high pressure magnet valve device |2 will be deenergized, and spring l2 therein will unseat the supply valve ll and seat the release valve lil. This will permit fluid at main reservoir pressure to ow past the valve 1| to the pipe i9, and from thence to the small area of the diaphragm 'l5 in the compensating valve device I3 within the seat rib '18. As before described, the spring 84 is strong enough to hold the diaphragm 15 seated on the seat rib T8 against full main reservoir pressure so long as only this small area is exposed to the high pressure.

From pipe 19 iluid under pressure also flows to the double check valve device 8| where it shifts the slide valve 82 to the right and flows to the main supply pipe 42. There is then available for effecting an application of the brakes fluid at a pressure of eighty pounds or greater.

If now the operator desires to effect either a service or an emergency application of the brakes he suitably manipulates the brake valve handle 88, or permits the controller handle ||5 to be moved to its upper position. The diaphragm 15 in the compensating valve device l5 will remain in the seated position illustrated until the pressure in brake cylinder pipe 44 has risen to some predetermined value sufficient to exert an upward differential ci pressure on diaphragm '|4 to unseat the diaphragm l5. When this takes place fluid main reservoir pressure flows past the unseated diaphragm 'l5 and to the high pressure pipe 8l. From pipe 8l the iiow is to the double check valve device 88, in which the slide valve 65 is shifted to the left and iluid then flows through pipe 63 and the passages heretofore described to the relay piston chamber 29. The relay valve will then function to establish a maximum brake cylinder pressure, which will correspond substantially to main reservoir pressure, namely eighty pounds or greater. The uid pressure brakes will be thus applied to the maximum possible degree.

Although fluid under pressure also flows to the track brake rheostat device 22 this device will not perform any useful function at this time because of the lack of available electric power for energizing the track brakes.

After an application of the brakes has been thus effected with the electric power supply off a release cannot be effected until the electric supply is again available to energize the high pressure magnet valve device I2, as the slide valve 85 of the double check valve 64 is maintained in the left hand position due to the high pressure of .the supply from pipe 8l, and brake cylinder pressure cannot be reduced by manipulation of the brake valve handle 85.

When the high pressure magnet valve device l2 is again energized, it seats its supply valve and unseats its release valve 70. Fluid under pressure is then released from the face of the relay valve piston 28 through the double check valve 68, the one-way check valve device 88 and exhaust port H8 in the high pressure magnet valve. In the double check valve device 8| the slide valve 82 will shift to the left as soon as the pressure in pipe 'i9 drops below the feed valve setting.

Thus once an application of the brakes has been effected with the electric power off, whether a service application or an emergency application, it cannot be released until electric power returns.

Modification of Fig. 2

The modification shown in Fig. 2 has to do principally with the employment f a new and diierent arrangement for making available the higher main reservoir pressure upon loss of electric power supply, and which permits a release at the brake valve. In this embodiment the control valve device of the previous embodiment, the same main reservoir i4 charged to the same degree as before, and the same feed valve device lli set for the same pressure value as before are all retained. A new high pressure magnet valve device |88 and a new compensating valve device lili replace the high pressure magnet valve device i2 and compensating magnet valve device I3 of the previous embodiment.

The high pressure magnet valve device |88 is embodied in a casing having a single supply valve |82 urged toward an unseated position by a spring |83 and toward a seated position by an electromagn'et |84.

The compensating valve device |8| is embodied in a casing having a valve |85 Which when unseated provides a by-pass communication around the feed valve device l5, as illustrated, and when seated closes this by-pass communication. The compensating valve device is also provided with a chamber |86 which is connected by way of pipe |81 and choke |88 to the main reservoir I4. When the pressure of uid in pipe |81' and chamber |85 is above a predetermined value, as for example thirty-live pounds, a Valve |89 will be actuated to upper seated position to open communication between chamber |88 and a chamber |98 above a diaphragm |9|. Diaphragm |8| will be then actuated downwardly to seat the valve |85.

When the pressure in chamber |88 and pipe |81 is reduced below the said predetermined value, valve |89 will move downwardly to cut oil supply to and vent the chamber |98, whereupon the diaphragm |9| will move upwardly and the valve |85 will be unseated. This will then permit fluid at main reservoir pressure to by-pass the feed valve device I and flow to the main supply pipe 42 through the one-way check valve device |93.

As long as the high pressure magnet valve device |88 remains energized pressure in pipe |87 and chamber |86 will be maintained at main reservoir pressure and valve 85 will be held seated. When however the high pressure magnet valve device is deenergized, as due to a loss of power supply or the trolley coming off, the

valve |82 will be unseated and the pressure in y pipe |81 and chamber |88 may be reduced, as will be now explained.

Connected to the high pressure magnet valve device above the valve |82 is a pipe |84 leading to the emergency pipe 58. Therefore, if after the high pressure magnet valve device has been deenergized an emergency application of the brakes should be effected, by reducing the pressure in the emergency pipe 58, the pressure in pipe |87 and chamber |86 would also be reduced by the oW of fluid past the valve |82 to the emergency pipe 58 and from thence to the atmosphere. The pressure in pipe |81 and chamber |88 would reduce faster than the resupply through choke |88 takes place, so that valve |85 in the compensating valve device would unseat and permit fluid at main reservoir pressure to flow to main supply pipe 42. An emergency application of the fluid pressure brakes would thus be effected to the maximum possible degree provided by main reservoir pressure.

In case it is desired to release the application, even though the electric supply remains cut off, this may be done by again charging the emergency pipe 58 and thus effecting the release as for the previously described emergency application. The emergency pipe will, of course, remain in communication with the main reservoir |4, so long as the high pressure magnet valve device remains deenergized. This may cause the emergency pipe to be charged to a degree higher than the setting of the feed valve device l5, but this is not undesirable.

It Will be seen therefore that in the embodiment of Fig. 2 the higher fluid pressure is available only for emergency applications, but a release may be readily effected after such an application even though the electric power remains off.

While I have described my invention with particular reference to two specific embodiments thereof it is not my intention to be limited to these embodiments or otherwise than by the spirit and scope of the appended claims.

` Having now described my invention, what I claim as new and desire to secure by Letters Patent, is:

l. A vehicle brake system comprising, in combination, at least one magnetic track brake device and at least one fluid pressure operated device for operating wheel brakes, control means for limiting to a moderate value the pressure of fluid supplied to operate said fluid pressure device so long as electric power is available to operate the magnetic track brake device, and means automatically operable to instantly make available fluid at a greatly increased pressure upon failure of the electric power.

2. In a vehicle brake equipment, in combination, an electric brake system, a J:luid pressure brake system, means for establishing fluid pressures below a limited value for effecting the operation of said magnetic track brake system and said fluid pressure brake system to produce a braking elect, and means operable in response to failure of the electric power provided for energizing the 'electric brake system for establishing fluid pressures above said limiting value so as to provide for an increased degree of braking by said fluid pressure brake system to at least partially compensate for the loss of braking by said electric brake system.

3. In a vehicle brake system, in combination, a brake cylinder, a magnetic track brake device, a fluid pressureoperated current controlling device or controlling the energization of said magnetic track brake device from a source of electric power, a pipe through which fluid underpressure is supplied to saidbrake cylinder and to said fluid pressure operated current controlling device, means operable 'to limit the maximum degree of fluid under pressure supplied through said pipe when making either service or emergency applications of the brakes, and means operative upon a failure of the electric power for making available fluid under pressure to a greatly increased degree.

4. In a vehicle brake system, in combination, a brake cylinder, a magnetic track brake device, a power circuit for supplying current to energize said magnetic track brake device, means for supplying uid under pressure to said brake cylinder to establish brake cylinder` pressures up to a chosen value, and electroresponsive means operable upon deenergization of said power circuit for making available fluid at an increased pressure whereby brake cylinder pressures may be established above said chosen value.

5. In a vehicle brake system, in combination, a brake cylinder, an electric brake device, a source of current supply for said electric brake device, means for supplying iiuid under pressure to said brake cylinder to -eifect a normal application of the brakes, a limiting valve device for limiting the maximum pressure of fluid thus supplied to said brake cylinder, and means operative upon a failure of said current supply for establishing a by-pass communication around said limiting'valve device whereby fluid at an increased-maximum pressure may iiow to said brake cylinder.

6. In a vehicle brake system, in combination,

. a brake cylinder, a valve device operable to supply fluid under pressure to said brake cylinder, a pressure limiting valve device for limiting the pressure of fluid supplied by said first mentioned valve device to said brake cylinder, an electric supplycircuit for supplying current to op ate an electric brake device, and elcctroresponsiv means operable upon deenergization of said supply cuit for making available for supply to said brake cylinder fluid at a pressure greater than permitted by said limiting valve device.

'7. In a vehicle brake system, in combination, a cylinder, valve means for supplying fluid under pressure to said brake cylinder, a mitng valve device for limiting the of thus supplied to said brake cylinder', a compensating valve device operable to make available fluid at an increased pressure for sup-ply to said brake cylinder, anda-magnet valve device operable when deenergized tc t operation of said ccmp-ensating Valve ce to make available said supply at said higher pressure.

8. In a vehicle brake system, in combination, a brake cylinder, a main reservoir, a valve device for supplying fluid under pressure to said brake cylinder, means establishing a communication through which said valve device supplies fluid under pressure from said main reservoir to said brake cylinder to a limited maximum degree only, a magnet valve device operable to open a communication through which iiuid at main reservoir pressure is made available for supply by said valve device to said brake cylinder, and a compensating valve device controlled in part by brake cylinder pressure and in part by main reservoir pressure for controlling the operation of said relay valve device.

9. In a vehicle brake system, in combination, a brake cylinder, an electric brake device, a source of current supply for said electric brake device, a relay Valve device for controlling the supply of fluid under pressure to and its release' from said brake cylinder, a main reservoir, a pressure limiting valve device for controlling a communication through which said relay valve device supplies uid under pressure from said main reservoir to said brake cylinder, said pressure limiting valve device limiting `the pressure of fluid thus supplied to a moderate value and less than main reservoir pressure, electroresponlsive means operable to establish a diiferent communication through which fluid at substantially main reservoir pressure is adapted to be supplied to said brake cylinder by said relay valve device, and a compensating valve device controlled in part by brake cylinder pressure and in part by said magnet valve device for controlling the operation of said relay valve device.

l0. In a vehicle brake system, in combination, a brake cylinder, a relay valve device having a chamber from which fluid under pressure may be supplied to said brake cylinder and having also valve means for opening communication between said chamber and said brake cylinder, a source of fluid under pressure, means establishing a communication between said source and said relay Valve chamber and being operable to limit the pressure of fluid supplied throughsaid communication to a chosen value, electroresponsive means operable when deenergized to supply fluid at a pressure higher than said chosen value to said chamber, and a valve device controlled in part by brake cylinder pressure and in part by the pressure of fluid at said higher pressure for controlling the operation of said relay valve means to establish a brake cylinder pressure corresponding to said higher pressure.

11. In a vehicle brake equipment, in combination, a fluid pressure brake system having a normally charged pipe and means operated upon a reduction of pressure in said pipe for effecting an application of the fluid pressure brakes, an electric brake system having a source of electric power supply, a pressure limiting valve device for limiting the pressure of fluid available for eiecting normal applications of the fluid pressure brakes, and means operable upon a failure of the electric power supply and a reduction of pressure in said normally charged pipe for establishing a by-pass communication around said pressure limiting Valve device through which fluid at a higher pressure may flow to provide an increased degree of application of the fluid pressure brakes.

12. In a vehicle brake system, in combination, a brake cylinder, a pressure limiting valve device for establishing a communication through which fluid at a limited maximum pressure may iloW, Valve means for supplying iluid under pressure from said communication to said brake cylinder, a normally charged pipe, a normally energized magnet valve device, and means operable upon deenergization of said magnet valve device and a reduction of pressure in said normally charged pipe for supplying fluid under pressure to said communication to a degree higher than permitted by said pressure limiting valve device.

13. In a vehicle brake system, in combination, a brake cylinder, an automatic valve device operable upon a reduction of fluid pressure therein to effect a supply of fluid under pressure to said brake cylinder, a valve device for limiting the pressure of fluid thus supplied to the brake cylinder, and electrically controlled means operable when deenergized and upon reduction of pressure in said automatic valve device for increasing the degree of fluid under pressure supplied to said brake cylinder.

CLYDE C. FARMER. 

